WO2023159408A1 - Dispositif de transmission composite mécanique-hydraulique multimode - Google Patents

Dispositif de transmission composite mécanique-hydraulique multimode Download PDF

Info

Publication number
WO2023159408A1
WO2023159408A1 PCT/CN2022/077552 CN2022077552W WO2023159408A1 WO 2023159408 A1 WO2023159408 A1 WO 2023159408A1 CN 2022077552 W CN2022077552 W CN 2022077552W WO 2023159408 A1 WO2023159408 A1 WO 2023159408A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
transmission
mechanical
hydraulic
brake
Prior art date
Application number
PCT/CN2022/077552
Other languages
English (en)
Chinese (zh)
Inventor
朱镇
盛杰
蔡英凤
陈龙
孙晓东
田翔
夏长高
张奕涵
后睿
Original Assignee
江苏大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 江苏大学 filed Critical 江苏大学
Priority to JP2023515614A priority Critical patent/JP2024509019A/ja
Priority to US18/025,653 priority patent/US11773954B1/en
Priority to GB2303896.1A priority patent/GB2614160A/en
Publication of WO2023159408A1 publication Critical patent/WO2023159408A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H2061/0075—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method
    • F16H2061/009—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method using formulas or mathematic relations for calculating parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H2061/0075—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method
    • F16H2061/0096—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method using a parameter map
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0095—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising four reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2058—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eleven engaging means

Definitions

  • the invention relates to the field of gearboxes, in particular to a multi-mode machine-hydraulic compound transmission device.
  • the multi-functional mechanical-hydraulic transmission device generally adopts hydraulic transmission to realize flexible high-torque start, mechanical transmission to complete high-efficiency transition, and mechanical-hydraulic compound transmission to meet the operating requirements of various working conditions within the entire speed regulation range of high-efficiency stepless speed regulation.
  • the common mechanical-hydraulic compound transmission is relatively easy to realize stepless speed regulation in each gear in the forward direction, but fails to fully consider the working condition adaptability of each gear in the reverse direction.
  • the mechanical-hydraulic compound transmission has an efficient stepless speed change function in the range of forward and reverse speed regulation. The use of multiple gears in a reasonable connection to realize the hydraulic-mechanical transmission mode can better solve this problem.
  • the present invention provides a multi-mode mechanical-hydraulic transmission device, which can switch modes of mechanical transmission, hydraulic transmission, and mechanical-hydraulic transmission through the combined switching of clutches and brakes.
  • a multi-mode mechanical-hydraulic transmission device which can switch modes of mechanical transmission, hydraulic transmission, and mechanical-hydraulic transmission through the combined switching of clutches and brakes.
  • the present invention achieves the above-mentioned technical purpose through the following technical means.
  • a multi-mode machine-hydraulic compound transmission device comprising an input member, a hydraulic transmission mechanism, a mechanical transmission mechanism, a converging mechanism, an output member, a clutch assembly and a brake assembly;
  • the clutch assembly connects the output end of the input mechanism to the hydraulic transmission mechanism respectively The input end, the mechanical transmission mechanism and the confluence mechanism are connected, the clutch assembly connects the output end of the hydraulic transmission mechanism with the confluence mechanism, and the clutch assembly connects the mechanical transmission mechanism with the confluence mechanism;
  • the confluence mechanism is connected with the output member;
  • a continuously variable gear ratio between the input member and the output member is provided by adjusting the displacement ratio of the hydraulic transmission, by selectively controlling the engagement of the clutch pack and the brake pack.
  • the mechanical transmission mechanism includes a mechanical transmission output shaft, a left planetary gear train and a right planetary gear train;
  • the left planetary gear train includes a left sun gear, a left planet carrier and a left ring gear
  • the right planet gear train has a right planet carrier, a right sun gear and a right ring gear
  • the left sun gear is connected with the right sun gear
  • the The right ring gear is connected with the left planetary carrier
  • the clutch assembly includes a fifth clutch C5 and a sixth clutch C6 ; the fifth clutch C5 is used to connect the right ring gear with the mechanical transmission output shaft, and the sixth clutch C6 is used to connect the right sun gear It is connected with the output shaft of the mechanical transmission; the brake assembly includes a second brake B 2 and a third brake B 3 , the second brake B 2 is used to connect the left ring gear with the fixed piece, and the third brake B 3 is used for To connect the right ring gear with the fixing piece.
  • the confluence mechanism includes a confluence mechanism left planetary gear train and a confluence mechanism right gear train;
  • the confluence mechanism left planetary gear train includes a confluence mechanism left planet carrier, a confluence mechanism left sun gear and a confluence mechanism left ring gear;
  • the confluence mechanism The right gear train of the mechanism includes the right sun gear of the confluence mechanism, the right planetary carrier of the confluence mechanism and the right ring gear of the confluence mechanism;
  • the left sun gear of the confluence mechanism is connected with the right sun gear of the confluence mechanism, and the left sun gear of the confluence mechanism is output to
  • the left ring gear of the converging mechanism is connected to the right planetary carrier of the converging mechanism;
  • the input member is connected to the left planetary carrier of the converging mechanism through the left gear pair and the right gear pair respectively;
  • the right ring gear of the converging mechanism is output through mechanical transmission
  • the gear pair is connected to the output shaft of the mechanical transmission
  • the clutch assembly also includes a third clutch C 3 , a fourth clutch C 4 and a seventh clutch C 7 ;
  • the third clutch C 3 is used to connect the input member to the input end of the converging mechanism through the left gear pair, the The fourth clutch C4 is used to connect the input member with the input end of the converging mechanism through the right gear pair;
  • the seventh clutch C7 is used to connect the right sun gear of the converging mechanism to the right planetary carrier of the converging mechanism;
  • the brake assembly is also Including the first brake B 1 and the fourth brake B 4 , the first brake B 1 is used to connect the left sun gear of the flow-combining mechanism with the fixed piece, and the fourth brake B 4 is used to connect the right ring gear of the flow-combination mechanism with the fixed piece .
  • the forward or reverse transmission mode between the input member and the output member includes: hydraulic transmission, mechanical transmission and mechanical transmission. Hydraulic compound transmission.
  • engaging the third clutch C 3 , the fourth clutch C 4 , the fifth clutch C 5 , the sixth clutch C 6 , the first brake B 1 , the second brake B 2 and the third brake B 3 provides the input member and the output Mechanical transmission with various transmission ratios forward or backward between components.
  • n o is the rotational speed of the output member
  • n I is the rotational speed of the input member
  • k 4 is the characteristic parameter of the right gear train of the confluence mechanism
  • i 6 i 7 is the transmission ratio between the output shaft of the mechanical transmission and the right ring gear of the confluence mechanism ;
  • k 1 is the characteristic parameter of the left planetary gear train
  • k 2 is the characteristic parameter of the right planetary gear train
  • Engaging the third clutch C3 and the seventh clutch C7 provides a forward mechanical transmission F(M3) between the input member and the output member, in which the rotational speeds of the input member and the output member satisfy the following relationship:
  • i 3 i 4 is the transmission ratio of the left gear pair
  • Engaging the sixth clutch C6 , the first brake B1 and the second brake B2 provides a forward mechanical transmission F(M4) between the input member and the output member in which the The rotational speed satisfies the following relationship:
  • a mechanical transmission R(M1) in reverse between the input member and the output member is provided, in which the input member and the output member
  • the rotational speed satisfies the following relationship:
  • k 3 is the characteristic parameter of the left gear train of the confluence mechanism; i 5 is the transmission ratio of the right gear pair.
  • the clutch assembly also includes a first clutch C 1 and a second clutch C 2 , the first clutch C 1 is used to connect the input member with the input end of the hydraulic transmission mechanism, and the second clutch C 2 is used to connect the The output end of the hydraulic transmission mechanism is connected to the left sun gear of the confluence mechanism; by adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C 1 , the second clutch C 2 , the seventh clutch C 7 and the fourth brake B 4 , A hydraulic transmission that provides multiple ratios of forward or reverse transmission between an input member and an output member.
  • hydraulic transmission F (H1 )/R(H1) in the hydraulic transmission F(H1)/R(H1), the speed of the input member and the output member satisfies the following relationship:
  • k 4 is the characteristic parameter of the right wheel train of the confluence mechanism; e is the displacement ratio of the hydraulic transmission mechanism; i 1 is the transmission ratio between the input end of the hydraulic transmission mechanism and the input member, and i 2 is the output end of the hydraulic transmission mechanism and the confluence
  • the transmission ratio between the left sun gears of the mechanism when e>0, it is F (H1) gear, and when e ⁇ 0, it is R (H1) gear;
  • Engaging the first clutch C 1 and the second clutch C 2 and the seventh clutch C 7 provides forward or reverse hydraulic transmission F(H2)/R(H2) between the input member and the output member, and the hydraulic transmission F(H2) In /R(H2), the rotational speeds of the input member and the output member satisfy the following relationship:
  • the second brake B 2 and the third brake B 3 provide a mechanical-hydraulic compound transmission with various transmission ratios forward or backward between the input member and the output member.
  • Hydraulic compound transmission F(HM1) in the mechanical-hydraulic compound transmission F(HM1), the rotational speeds of the input member and the output member satisfy the following relationship:
  • Progressive mechatronic recombination between the input member and the output member is provided by adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C 1 , the second clutch C 2 , the sixth clutch C 6 and the second brake B 2 Transmission F(HM4), in the mechanical-hydraulic compound transmission F(HM4), the speeds of the input member and the output member satisfy the following relationship:
  • Reverse fluid between the input member and the output member is provided by adjusting the displacement ratio of the hydraulic transmission assembly, by engaging the first clutch C 1 , the second clutch C 2 , the fifth clutch C 5 , and the second brake B 2
  • Compound transmission R(HM1), in the mechanical-hydraulic compound transmission R(HM1), the speeds of the input member and the output member satisfy the following relationship:
  • the multi-mode machine-hydraulic transmission device described in the present invention adopts three modes of hydraulic transmission, mechanical transmission and machine-hydraulic transmission with 14 gears to meet the requirements of complex operations; both hydraulic transmission gears and machine-hydraulic transmission gears can be realized
  • the non-power interrupted shifting of gears can also realize the stepless speed regulation between the gears of the mechanical hydraulic transmission; the speed regulation range of the forward and reverse directions is expanded, and the degree of freedom of adjustment is expanded.
  • Fig. 1 is the schematic structural diagram of the multi-mode machine-hydraulic compound transmission device of the present invention
  • Fig. 2 is a schematic diagram of the power flow of the mechanical transmission F (M1) gear of the present invention
  • Fig. 3 is a schematic diagram of the power flow of the mechanical transmission F (M2) gear of the present invention
  • Fig. 4 is a schematic diagram of the power flow of the mechanical transmission F (M3) gear of the present invention.
  • Fig. 5 is a schematic diagram of the power flow of the mechanical transmission F (M4) gear of the present invention.
  • Fig. 6 is a schematic diagram of the power flow of the mechanical transmission R (M1) gear of the present invention.
  • Fig. 7 is a schematic diagram of the power flow of the mechanical transmission R (M2) gear of the present invention.
  • Fig. 8 is a schematic diagram of the power flow of the hydraulic transmission F(H1)/R(H1) gear of the present invention.
  • Fig. 9 is a schematic diagram of the power flow of the hydraulic transmission F(H2)/R(H2) gear of the present invention.
  • Fig. 10 is a schematic diagram of the power flow of gear F (HM1) of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 11 is a schematic diagram of the power flow of F (HM2) gear of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 12 is a schematic diagram of the power flow of F (HM3) gear of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 13 is a schematic diagram of the power flow of gear F (HM4) of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 14 is a schematic diagram of the power flow of gear R (HM1) of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 15 is a schematic diagram of the power flow of R (HM2) gear of the mechanical-hydraulic compound transmission of the present invention
  • Fig. 16 is a curve diagram of each gear mode switch and its speed regulation characteristic in the present invention.
  • first and second are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, a feature defined as “first” or “second” may explicitly or implicitly include one or more of these features.
  • “plurality” means two or more, unless otherwise specifically defined.
  • the multi-mode machine-hydraulic compound transmission device of the present invention includes an input shaft 1, a mechanical transmission mechanism 2, an output shaft 3, a converging mechanism 4, an intermediate shaft 5, a hydraulic transmission mechanism 6, a clutch assembly and a brake components;
  • the hydraulic transmission mechanism 6 includes a hydraulic transmission input gear pair 6-1, a hydraulic transmission input shaft 6-2, a first clutch C 1 6-3, a variable pump 6-4, a hydraulic pipeline 6-5, and a second clutch C 2 6-6, hydraulic transmission output shaft 6-7, quantitative motor 6-8, hydraulic transmission output gear pair 6-9 and the first brake B 1 6-10; the first clutch C 1 6-3 is used to connect the input Shaft 1 and hydraulic transmission input shaft 6-2, the second clutch C 2 6-6 is used to connect the hydraulic transmission output shaft 6-7 and the intermediate shaft 5, and the first brake B 1 6-10 is used for braking Intermediate shaft 5.
  • the mechanical transmission mechanism 2 includes a left sun gear 2-5, a left planet carrier 2-6, a second brake B 2 2-7, a left ring gear 2-8, a right planet carrier 2-9, and a right sun gear 2-10 , the third brake B 3 2-11, the right ring gear 2-12, the fifth clutch C 5 2-13, the sixth clutch C 6 2-14, the mechanical transmission output shaft 2-15 and the mechanical transmission output gear pair 2- 16.
  • the left planetary gear train includes a left sun gear 2-5, a left planetary carrier 2-6 and a left ring gear 2-8
  • the right planetary gear train has a right planetary gear 2-9, a right sun gear 2-10 and
  • the right ring gear 2-12 the left sun gear 2-5 is connected with the right sun gear 2-10
  • the right ring gear 2-12 is connected with the left planet carrier 2-6
  • the fifth clutch C 5 2- 13 is used to connect the right ring gear 2-12 with the mechanical transmission output shaft 2-15
  • the sixth clutch C 6 2-14 is used to connect the right sun gear 2-10 with the mechanical transmission output shaft 2-15, so
  • the simultaneous engagement of the fifth clutch C 5 2-13 and the sixth clutch C 6 2-14 can firmly connect the mechanical transmission mechanism 2
  • the second brake B 2 2-7 is used to connect the left ring gear 2-8 Connected with the fixed part
  • the third brake B 3 2-11 is used to connect the right ring gear 2-12 with the fixed part.
  • the converging mechanism 4 includes the left planetary gear train of the converging mechanism, the right gear train of the converging mechanism, the first brake B 1 6-10, the fourth brake B 4 4-6, the third clutch C 3 2-2, and the fourth clutch C 4 2-4 and the seventh clutch C 7 4-8;
  • the left planetary gear train of the converging mechanism includes the left planet carrier 4-1 of the converging mechanism, the left sun gear 4-2 of the converging mechanism and the left ring gear 4-3 of the converging mechanism;
  • the right gear train of the converging mechanism includes the right sun gear 4-4 of the converging mechanism, the right planet carrier 4-5 of the converging mechanism and the right ring gear 4-7 of the converging mechanism;
  • Wheel 4-4 is connected, the left sun gear 4-2 of the confluence mechanism is connected with the intermediate shaft 5, the left sun gear 4-2 of the confluence mechanism is connected with the output end of the hydraulic transmission mechanism 6;
  • the left ring gear 4-2 of the confluence mechanism is 3 is connected with the right
  • Engage third clutch C 3 2-2, fourth clutch C 4 2-4, fifth clutch C 5 2-13, sixth clutch C 6 2-14, first brake B 1 6-10, second brake B 2 2-7 and the third brake B 3 2-11 provide mechanical transmission of various transmission ratios forward or backward between the input member and the output member.
  • the power flow of the mechanical transmission F (M1) is shown in Figure 2, and only the fifth clutch C 5 2-13, the sixth clutch C 6 2-14 and the first brake B 1 6-10 are engaged.
  • the power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1 and the mechanical transmission mechanism 2 that is solidly connected as one, and is transmitted to the right ring gear 4-7 of the confluence mechanism through the mechanical transmission output gear pair 2-16, and the power is transmitted to the right ring gear 4-7 of the confluence mechanism through the confluence mechanism.
  • the planet carrier 4-5 is output from the output shaft 3.
  • the relationship between output speed and input speed is:
  • n o is the rotational speed of the output member
  • n I is the rotational speed of the input member
  • k 4 is the characteristic parameter of the right gear train of the confluence mechanism
  • i 6 i 7 are the output shaft 2-15 of the mechanical transmission and the right ring gear 4- Transmission ratio between 7;
  • the power flow of the mechanical transmission F (M2) is shown in Fig. 3, and only the sixth clutch C 6 2-14, the first brake B 1 6-10 and the third brake B 3 2-11 are engaged.
  • the power is diverted to the right planetary carrier 2-9 and the right sun gear 2-10 through the input shaft 1, the left planetary carrier 2-6, and then converged to the mechanical transmission output shaft 2-15 through the right sun gear 2-10, and then passed through the mechanical transmission output gear
  • the auxiliary 2-16 is transmitted to the right ring gear 4-7 of the converging mechanism, and the power is output from the output shaft 3 through the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • k 1 is the characteristic parameter of the left planetary gear train
  • k 2 is the characteristic parameter of the right planetary gear train.
  • the power flow of the mechanical transmission F (M3) is shown in Fig. 4, only the third clutch C 3 2-2 and the seventh clutch C 7 4-8 are engaged.
  • the power is transmitted to the left planet carrier 4-1 of the confluence mechanism through the input shaft 1 and the left gear pair 2-1, and is output from the output shaft 3 through the confluence mechanism 4 which is fixedly connected as one.
  • the relationship between output speed and input speed is:
  • i 3 i 4 is the transmission ratio of the left gear pair 2-1;
  • the power flow of the mechanical transmission F (M4) is shown in Fig. 5, and only the sixth clutch C 6 2-14, the first brake B 1 6-10 and the second brake B 2 2-7 are engaged.
  • the power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1, the left planet carrier 2-6, the left sun gear 2-5 and the right sun gear 2-10, and is transmitted to the right side of the confluence mechanism through the mechanical transmission output gear pair 2-16.
  • the ring gear 4-7, the power is output from the output shaft 3 through the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical transmission R (M1) is shown in Fig. 6, only the fifth clutch C 5 2-13, the first brake B 1 6-10 and the second brake B 2 2-7 are engaged.
  • the power is transmitted to the mechanical transmission output shaft 2-15 through the input shaft 1, the left planetary carrier 2-6, the left sun gear 2-5, the right sun gear 2-10 and the right ring gear 2-12, and then through the mechanical transmission output gear pair 2 -16 is transmitted to the right ring gear 4-7 of the converging mechanism, and the power is output from the output shaft 3 through the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical transmission R (M2) is shown in Fig. 7, only the fourth clutch C4 2-4 and the first brake B1 6-10 are engaged.
  • the power is transmitted to the left planetary carrier 4-1 of the confluence mechanism through the input shaft 1 and the left and right gear pairs 2-3, and then output from the output shaft 3 through the left ring gear 4-3 of the confluence mechanism and the right planetary carrier 4-5 of the mechanism.
  • the relationship between output speed and input speed is:
  • k 3 is the characteristic parameter of the left gear train of the confluence mechanism; i 5 is the transmission ratio of the right gear pair 2-3.
  • a hydraulic transmission that provides multiple ratios of forward or reverse transmission between an input member and an output member.
  • the power flow of the hydraulic transmission F(H1)/R(H1) is shown in Figure 8, and only the first clutch C 1 6-3, the second clutch C 2 6-6 and the fourth brake B 4 4-6 are engaged.
  • the power is transmitted to the hydraulic transmission input shaft 6-2 to drive the variable pump 6-4 through the input shaft 1 and the hydraulic transmission input gear pair 6-1, and the oil fluid passes through the hydraulic pipeline 6-5 to drive the quantitative motor 6-8 to drive the hydraulic transmission output Axle 6-7, power is output from output shaft 3 through hydraulic transmission output gear pair 6-9, converging mechanism right sun gear 4-4 and converging mechanism right planet carrier 4-5.
  • the relationship between output speed and input speed is:
  • k 4 is the characteristic parameter of the right wheel train of the confluence mechanism; e is the displacement ratio of the hydraulic transmission mechanism 6; i 1 is the transmission ratio between the input end of the hydraulic transmission mechanism 6 and the input member, and i 2 is the output of the hydraulic transmission mechanism 6
  • the power flow of the hydraulic transmission F(H2)/R(H2) is shown in Figure 9, only the first clutch C 1 6-3, the second clutch C 2 6-6 and the seventh clutch C 7 4-8 are engaged.
  • the power is transmitted to the hydraulic transmission input shaft 6-2 to drive the variable pump 6-4 through the input shaft 1 and the hydraulic transmission input gear pair 6-1, and the oil fluid passes through the hydraulic pipeline 6-5 to drive the quantitative motor 6-8 to drive the hydraulic transmission output Axle 6-7, power is output from output shaft 3 through hydraulic transmission output gear pair 6-9, converging mechanism 4 that is solidly connected as one.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical-hydraulic compound transmission F (HM1) is shown in Figure 10, only the first clutch C 1 6-3, the second clutch C 2 6-6, the fifth clutch C 5 2-13 and the sixth clutch C 6 are engaged 2-14.
  • the power is shunted through the input shaft 1, and one way is transmitted to the mechanical transmission output shaft 2-15 through the solidly connected mechanical transmission mechanism 2, and then transmitted to the right ring gear 4-7 of the confluence mechanism through the mechanical transmission output gear pair 2-16; It is transmitted to the right sun gear 4-4 of the converging mechanism through the hydraulic transmission mechanism 6.
  • the mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after converging at the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical-hydraulic compound transmission F is shown in Figure 11, and only the first clutch C 1 6-3, the second clutch C 2 6-6 and the third clutch C 3 2-2 are engaged.
  • the power is split through the input shaft 1, and one path is transmitted to the left planet carrier 4-1 of the confluence mechanism through the left gear pair 2-1; the other path is transmitted to the left sun gear 4-2 of the confluence mechanism through the hydraulic transmission mechanism 6.
  • the mechanical power transmitted to the planetary carrier 4-1 and the hydraulic power transmitted to the left sun gear 4-2 are merged by the left ring gear 4-3 of the converging mechanism, and output from the output shaft 3 by the right planetary carrier 4-5 of the converging mechanism .
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical-hydraulic compound transmission F (HM3) is shown in Figure 12, only the first clutch C 1 6-3, the second clutch C 2 6-6, the sixth clutch C 6 2-14 and the third brake B 3 are engaged 2-11.
  • the power is divided through the input shaft 1, and all the way is divided through the left planetary carrier 2-6 to the right planetary carrier 2-9 and the right sun gear 2-10, and then converged to the mechanical transmission output shaft 2-15 through the right sun gear 2-10.
  • the transmission output gear pair 2-16 is transmitted to the right ring gear 4-7 of the confluence mechanism; the other path is transmitted to the right sun gear 4-4 of the confluence mechanism through the hydraulic transmission mechanism 6.
  • the mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after converging at the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after converging at the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical-hydraulic compound transmission R (HM1) is shown in Figure 14, only the first clutch C 1 6-3, the second clutch C 2 6-6, the fifth clutch C 5 2-13, and the second brake B are engaged 2 2-7.
  • the power is split through the input shaft 1, and one way is transmitted to the mechanical transmission output shaft 2-15 through the left planet carrier 2-6, the left sun gear 2-5, the right sun gear 2-10 and the right ring gear 2-12.
  • the transmission output gear pair 2-16 is transmitted to the right ring gear 4-7 of the confluence mechanism; the other path is transmitted to the right sun gear 4-4 of the confluence mechanism through the hydraulic transmission mechanism 6.
  • the mechanical power transmitted to the right ring gear 4-7 of the converging mechanism and the hydraulic power transmitted to the right sun gear 4-4 of the converging mechanism are output from the output shaft 3 after converging at the right planet carrier 4-5 of the converging mechanism.
  • the relationship between output speed and input speed is:
  • the power flow of the mechanical-hydraulic compound transmission RHM2 is shown in Figure 15, and only the first clutch C 1 6-3, the second clutch C 2 6-6 and the fourth clutch C 4 2-4 are engaged.
  • the power is split through the input shaft 1, and one path is transmitted to the left planet carrier 4-1 of the confluence mechanism through the right gear pair 2-3; the other path is transmitted to the left sun gear 4-2 of the confluence mechanism through the hydraulic transmission mechanism 6.
  • the mechanical power transmitted to the planetary carrier 4-1 and the hydraulic power transmitted to the left sun gear 4-2 are merged by the left ring gear 4-3 of the converging mechanism, and output from the output shaft 3 by the right planetary carrier 4-5 of the converging mechanism .
  • the relationship between output speed and input speed is:
  • i 1 i 2 1.00
  • Figure 16 shows the relationship between the ratio of the output speed to the input speed of the transmission and the displacement ratio, and the output shaft can be connected to the reduction gear to drive the vehicle.
  • O is the origin
  • n o en I , when e ⁇ [-1.00, 1.00], n o /n e ⁇ [-1.00, 1.00];
  • the H1 gear is used instead of the H2 gear, but the H2 gear cannot be switched to the mechanical-hydraulic compound transmission gear without power interruption.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

La présente invention concerne un dispositif de transmission composite mécanique-hydraulique multimode, comprenant un composant d'entrée, un mécanisme de transmission hydraulique, un mécanisme de transmission mécanique, un mécanisme de confluence, un composant de sortie, un ensemble embrayage et un ensemble frein. L'ensemble embrayage relie une extrémité de sortie de l'élément d'entrée respectivement à une extrémité d'entrée du mécanisme de transmission hydraulique, du mécanisme de transmission mécanique et du mécanisme de confluence, l'ensemble embrayage relie une extrémité de sortie du mécanisme de transmission hydraulique au mécanisme de confluence, et l'ensemble embrayage relie le mécanisme de transmission mécanique au mécanisme de confluence. Le mécanisme de confluence est relié au composant de sortie. Un rapport de transmission à variation continue entre le composant d'entrée et le composant de sortie est fourni par réglage d'un rapport de déplacement du mécanisme de transmission hydraulique et par commande sélective de la mise en prise entre l'ensemble embrayage et l'ensemble frein. Selon la présente invention, la commutation de modes tels qu'une transmission mécanique, une transmission hydraulique et une transmission composite mécanique-hydraulique peut être mise en œuvre, ce qui permet d'augmenter le degré de liberté de réglage tandis que la performance tolérante aux défaillances d'un système est améliorée, et d'étendre la plage de régulation de vitesse dans des directions d'avance et de recul.
PCT/CN2022/077552 2022-02-22 2022-02-24 Dispositif de transmission composite mécanique-hydraulique multimode WO2023159408A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2023515614A JP2024509019A (ja) 2022-02-22 2022-02-24 マルチモードの機械液圧複合伝動装置
US18/025,653 US11773954B1 (en) 2022-02-22 2022-02-24 Multi-mode hydro-mechanical hybrid transmission device
GB2303896.1A GB2614160A (en) 2022-02-22 2022-02-24 Multi-mode hydro-mechanical hybrid transmission device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202210163801.4 2022-02-22
CN202210163801.4A CN115076327A (zh) 2022-02-22 2022-02-22 一种多模式机液复合传动装置

Publications (1)

Publication Number Publication Date
WO2023159408A1 true WO2023159408A1 (fr) 2023-08-31

Family

ID=83246134

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/077552 WO2023159408A1 (fr) 2022-02-22 2022-02-24 Dispositif de transmission composite mécanique-hydraulique multimode

Country Status (2)

Country Link
CN (1) CN115076327A (fr)
WO (1) WO2023159408A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2024509019A (ja) * 2022-02-22 2024-02-29 江▲蘇▼大学 マルチモードの機械液圧複合伝動装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170166183A1 (en) * 2015-12-14 2017-06-15 Hyundai Motor Compan Apparatus for controlling transmission system of hybrid electric vehicle and method thereof
CN111946794A (zh) * 2020-07-20 2020-11-17 江苏大学 一种具有自动调节功能的功率分流式机液复合传动系统
CN111946792A (zh) * 2020-07-20 2020-11-17 江苏大学 一种功率分流和功率汇流相结合的机液复合传动装置
CN113137462A (zh) * 2021-05-18 2021-07-20 吉林大学 一种作业车辆的行走传动装置及其控制方法
CN113147378A (zh) * 2021-05-18 2021-07-23 吉林大学 一种多模式机械液压传动装置及其控制方法
CN114001139A (zh) * 2021-10-27 2022-02-01 江苏大学 一种包含单泵多马达系统的机液复合传动装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170166183A1 (en) * 2015-12-14 2017-06-15 Hyundai Motor Compan Apparatus for controlling transmission system of hybrid electric vehicle and method thereof
CN111946794A (zh) * 2020-07-20 2020-11-17 江苏大学 一种具有自动调节功能的功率分流式机液复合传动系统
CN111946792A (zh) * 2020-07-20 2020-11-17 江苏大学 一种功率分流和功率汇流相结合的机液复合传动装置
CN113137462A (zh) * 2021-05-18 2021-07-20 吉林大学 一种作业车辆的行走传动装置及其控制方法
CN113147378A (zh) * 2021-05-18 2021-07-23 吉林大学 一种多模式机械液压传动装置及其控制方法
CN114001139A (zh) * 2021-10-27 2022-02-01 江苏大学 一种包含单泵多马达系统的机液复合传动装置

Also Published As

Publication number Publication date
CN115076327A (zh) 2022-09-20

Similar Documents

Publication Publication Date Title
RU2328641C2 (ru) Гидромеханическая трансмиссия, воспроизводящая четыре режима работы
WO2020147141A1 (fr) Système de transmission à variation continue réalisant une commutation multimode de puissance hybride
CN111946792B (zh) 一种功率分流和功率汇流相结合的机液复合传动装置
CN102943859B (zh) 一种装载机用液压机械无级变速器
CN113147378B (zh) 一种多模式机械液压传动装置及其控制方法
CN106415064B (zh) 用于机动车的变速器
CN109764107B (zh) 一种变速传动装置
US9145928B2 (en) Transmission with rear torque converter
CN113137462B (zh) 一种作业车辆的行走传动装置及其控制方法
CN109764123B (zh) 一种行星齿轮特性参数可变的多模式切换动力传动系统
WO2022027723A1 (fr) Dispositif de transmission composite à engrenage et hydraulique à double anneau
WO2023159408A1 (fr) Dispositif de transmission composite mécanique-hydraulique multimode
CN112128338A (zh) 一种双液压传动机构参与的机液复合传动装置
JP2017075692A (ja) 遊星歯車セットを備えて少なくとも３つの走行レンジを有する無段のパワースプリット型変速機
WO2022027724A1 (fr) Transmission à variation continue multimode à vitesse de rotation et couplage de couple
CN107246467B (zh) 装载机液压机械无级传动装置
US20220145972A1 (en) Power-split hydro-mechanical hybrid transmission system with automatic adjustment function
WO2023236127A1 (fr) Dispositif d'entraînement composite mécanique-électrique-hydraulique et son procédé de commande
WO2023130420A1 (fr) Dispositif de transmission à variation continue ayant à la fois une sortie à différence égale et une sortie à rapport égal
US7335125B2 (en) Continuously variable transmission
JP7271036B2 (ja) 歯車－二重環状－液圧の複合伝動装置
GB2619182A (en) Hydro-mechanical series and parallel transmission device and control method thereof
CN109519513B (zh) 一种工程机械及其液压机械复合变速箱
US20200370630A1 (en) Continuously variable power-split transmission
CN219838440U (zh) 车辆动力系统、车辆

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 2023515614

Country of ref document: JP

ENP Entry into the national phase

Ref document number: 202303896

Country of ref document: GB

Kind code of ref document: A

Free format text: PCT FILING DATE = 20220224

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22927699

Country of ref document: EP

Kind code of ref document: A1